EP2602487B1 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP2602487B1
EP2602487B1 EP10846307.6A EP10846307A EP2602487B1 EP 2602487 B1 EP2602487 B1 EP 2602487B1 EP 10846307 A EP10846307 A EP 10846307A EP 2602487 B1 EP2602487 B1 EP 2602487B1
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EP
European Patent Office
Prior art keywords
oil supply
passage
rotor
pump chamber
axial direction
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10846307.6A
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German (de)
English (en)
Other versions
EP2602487A1 (fr
EP2602487A4 (fr
Inventor
Ryuichi Sakakibara
Kikuji Hayashida
Kiyotaka Ohtahara
Yoshimasa Kuno
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Taiho Kogyo Co Ltd
Original Assignee
Taiho Kogyo Co Ltd
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Publication date
Application filed by Taiho Kogyo Co Ltd filed Critical Taiho Kogyo Co Ltd
Publication of EP2602487A1 publication Critical patent/EP2602487A1/fr
Publication of EP2602487A4 publication Critical patent/EP2602487A4/fr
Application granted granted Critical
Publication of EP2602487B1 publication Critical patent/EP2602487B1/fr
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a vane pump and, more particularly, to a vane pump in which an oil supply passage through which a lubricating oil flows is formed inside a rotor, and in which the lubricating oil is intermittently supplied in a pump chamber by a rotation of the rotor.
  • a vane pump which includes: a housing including a substantially circular pump chamber; a rotor that rotates about a position eccentric with respect to a center of the pump chamber; a vane that is rotated by the rotor and that always partitions the pump chamber into a plurality of spaces; an oil supply passage that intermittently communicates with the pump chamber by the rotation of the rotor; an oil supply pipe that is connected to this oil supply passage to supply a lubricating oil from a hydraulic pump thereto; and a gas passage that makes the pump chamber and an outer space communicate with each other when the oil supply passage communicates with the pump chamber by the rotation of the rotor, wherein the oil supply passage includes: a diameter direction oil supply hole provided at a shaft part of the rotor in a diameter direction thereof; and an axial direction oil supply groove that is provided in the housing to communicate with the pump chamber, and with which an opening of the diameter direction oil supply hole is made to intermittently overlappingly communicate by the rotation of the rotor, and wherein
  • the diameter direction gas hole of the gas passage is adapted to communicate with the axial direction gas groove at the same time, so as to allow the air of the outer space to flow into the pump chamber through the gas passage.
  • Patent Document 1 Japanese Patent Laid-Open No. 2006-226164
  • the present invention provides a vane pump in which even though a hydraulic pressure of a lubricating oil supplied from a hydraulic pump to an oil supply passage is low, the air is prevented from being sucked into a pump chamber from a gas passage as much as possible, and thereby engine driving torque can be prevented from increasing.
  • the present invention is a vane pump including: a housing including a substantially circular pump chamber; a rotor that rotates about a position eccentric with respect to a center of the pump chamber; a vane that is rotated by the rotor and that always partitions the pump chamber into a plurality of spaces; an oil supply passage that intermittently communicates with the pump chamber by the rotation of the rotor; an oil supply pipe that is connected to this oil supply passage to supply a lubricating oil from a hydraulic pump thereto; and a gas passage that makes the pump chamber and an outer space communicate with each other when the oil supply passage communicates with the pump chamber by the rotation of the rotor, wherein the oil supply passage includes: a diameter direction oil supply hole provided at a shaft part of the rotor in a diameter direction thereof; and an axial direction oil supply groove that is provided in the housing to communicate with the pump chamber, and with which an opening of the diameter direction oil supply hole is made to intermittently overlappingly communicate by the rotation of the rotor, and wherein the
  • the passage area S 1 of the gas passage is set to be as small a passage area S 1 as possible in order to reduce the leakage of the lubricating oil to the outer space through the gas passage, i.e., to an internal space of an engine, when the hydraulic pressure of the lubricating oil supplied from the hydraulic pump to the oil supply passage is high.
  • the passage area S 2 of the oil supply passage is set to be in the range of S 1 ⁇ S 2 ⁇ 3 ⁇ S 1 .
  • the passage area S 2 of the oil supply passage is set to be a relatively small passage area that is at most three times larger than the passage area S 1 that is as small as possible of the gas passage to thereby make the air difficult to be sucked.
  • the passage area S 2 of the oil supply passage disclosed in Figure 3 of the above-described Patent Document 1 is set to be approximately sixteen times as large as the passage area S 1 of the gas passage, which is a comparison based on a drawing.
  • the passage area S 2 of the oil supply passage is set to be larger than the passage area S 1 of the gas passage, so that the required lubricating oil is reliably supplied in the pump chamber during operation beyond idling of the vane pump.
  • the passage area S 3 of the oil supply pipe is set to be in the range of S 2 ⁇ S 3 ⁇ 3 ⁇ S 2 with respect to the passage area S 2 of the oil supply passage set to be relatively small. This is because a squeezing effect can be obtained by making the passage area S 3 of the oil supply pipe larger than the passage area S 2 of the oil supply passage, and thereby a hydraulic pressure in the oil supply passage can be kept as high as possible even with a small amount of lubricating oil at the time of idling.
  • the width L of the axial direction oil supply groove is set to be in the range of d 2 ⁇ L ⁇ 4 ⁇ d 2 .
  • the opening of the diameter direction oil supply hole intermittently crosses the axial direction oil supply groove by the rotation of the rotor, and when crossing it, the opening is overlapped to be in communication with the groove.
  • a time of communication i.e., an overlap time
  • the width L of the axial direction oil supply groove is set to be in the above-described range to thereby suppress suck of the air.
  • Figures 1 and 2 show a vane pump 1 according to the present invention, and this vane pump 1 is fixed to a side surface of an engine of an automobile, which is not shown, to generate a negative pressure in a servo unit for a brake system, which is not shown.
  • This vane pump 1 includes: a housing 2 in which a substantially circular pump chamber 2A is formed; a rotor 3 that is rotated by an engine drive force about a position eccentric with respect to a center of the pump chamber 2A; a vane 4 that is rotated by the rotor 3 and that always partitions the pump chamber 2A into a plurality of spaces; and a cover 5 that closes the pump chamber 2A.
  • the housing 2 is provided with an intake air passage 6 that communicates with the servo unit for the brake to suck a gas from the servo unit, the intake air passage 6 being located at an upper part of the pump chamber 2A, and a discharge passage 7 for discharging the gas sucked from the servo unit, the discharge passage 7 being located at a lower part of the pump chamber 2A, respectively. Additionally, the intake air passage 6 is provided with a check valve 8 in order to hold a negative pressure in the servo unit particularly when the engine is stopped.
  • the rotor 3 includes a cylindrical rotor part 3A that rotates in the pump chamber 2A, an outer periphery of the rotor part 3A is provided so as to contact with an inner peripheral surface of the pump chamber 2A, the intake air passage 6 is located at an upstream side with respect to a rotation of the rotor part 3A, and the discharge passage 7 is formed closer to a downstream side than the rotor part 3A.
  • a groove 9 is formed in a diameter direction at the rotor part 3A, and the vane 4 is slidably moved in a direction perpendicular to an axial direction of the rotor 3 along the groove 9.
  • a lubricating oil from an oil supply passage which will be described hereinafter, flows between a hollow part 3a formed in a center of the rotor part 3A and the vane 4.
  • caps 4a are provided at both ends of the vane 4, and the pump chamber 2A is always partitioned into two or three spaces by rotating these caps 4a while always sliding them on the inner peripheral surface of the pump chamber 2A.
  • the pump chamber 2A is partitioned by the vane 4 into an illustrated horizontal direction in a state of Figure 1 , further, the pump chamber is partitioned by the rotor part 3A into a vertical direction in a space of an illustrated right side, and therefore, the pump chamber 2A is partitioned into a total of three spaces.
  • the pump chamber 2A is partitioned into two spaces: a space of an intake air passage 6 side; and a space of a discharge passage 7 side.
  • Figure 2 shows a cross-sectional view of a II-II part in the above-described Figure 1 , a bearing part 2B for pivotally supporting a shaft part 3B constituting the rotor 3 is formed at an illustrated right side of the pump chamber 2A in the housing 2, and the shaft part 3B rotates integrally with the rotor part 3A.
  • the cover 5 is provided at a left end of the pump chamber 2A, the rotor part 3A and an end surface of an illustrated left side of the vane 4 rotate slidingly contacting with this cover 5, and additionally, an end surface of a right side of the vane 4 rotates slidingly contacting with an inner surface of a bearing part 2B side of the pump chamber 2A.
  • a bottom surface 9a of the groove 9 formed in the rotor 3 is formed slightly closer to a shaft part 3B side than the surface with which the pump chamber 2A and the vane 4 slidingly contact, and a gap is formed between the vane 4 and the bottom surface 9a.
  • shaft part 3B projects to the illustrated right side more than the bearing part 2B of the housing 2, couplings 10 rotated by an engine cam shaft are coupled at this projecting position, and the rotor 3 is rotated by a rotation of the cam shaft.
  • an oil supply passage 11 through which the lubricating oil is flowed is formed at the shaft part 3B, and this oil supply passage 11 is connected to a hydraulic pump driven by an engine, which is not shown, through an oil supply pipe 12.
  • the oil supply passage 11 includes: an axial direction oil supply hole 11a formed in an axial direction of the shaft part 3B; and a diameter direction oil supply hole 11b perforated in a diameter direction of the shaft part 3B, the hole 11b communicating with this axial direction oil supply hole 11a.
  • an axial direction oil supply groove 11c constituting the oil supply passage 11 formed so as to make the pump chamber 2A and the diameter direction oil supply hole 11b communicate with a sliding part with the shaft part 3B, and the axial direction oil supply groove 11c is formed at an upper part of the bearing part 2B shown in Figure 2 in the embodiment.
  • the vane pump 1 of the embodiment includes a gas passage 13 that makes the pump chamber 2A communicate with an outer space when the oil supply passage 11 is made to communicate with the pump chamber 2A by the rotation of the rotor 3, and more specifically, when the opening of the diameter direction oil supply hole 11b overlaps the axial direction oil supply groove 11c.
  • the gas passage 13 includes a diameter direction gas hole 13a perforated in the shaft part 3B by penetrating the axial direction oil supply hole 11a constituting the oil supply passage 11, and this diameter direction gas hole 13a is formed at a place displaced from the diameter direction oil supply hole 11b of the oil supply passage 11 by 90 degrees.
  • a position of this axial direction gas groove 13b is formed at a position rotated along the bearing part 2B by 90 degrees with respect to the axial direction oil supply groove 11c, and thus, at the same time when the diameter direction oil supply hole 11b of the oil supply passage 11 communicates with the axial direction oil supply groove 11c, the diameter direction gas hole 13a communicates with the axial direction gas groove 13b.
  • a volume in the space of the intake air passage 6 side partitioned by the vane 4 increases to generate a negative pressure in the pump chamber 2A, and a gas is sucked from the servo unit through the intake air passage 6 to generate a negative pressure in the servo unit.
  • the sucked gas is then compressed due to decrease of a volume of the space of the discharge passage 7 side, and it is discharged from the discharge passage 7.
  • the lubricating oil is supplied to the oil supply passage 11 from the hydraulic pump driven by the engine through the oil supply pipe 12, and this lubricating oil flows into the pump chamber 2A when the diameter direction oil supply hole 11b and the axial direction oil supply groove 11c of the housing 2 communicate with each other by the rotation of the rotor 3.
  • the lubricating oil having flowed into the pump chamber 2A flows into the hollow part 3a of the rotor part 3A from the gap between the bottom surface 9a of the groove 9 part formed at the rotor part 3A and the vane 4, this lubricating oil spouts in the pump chamber 2A from the gap between the vane 4 and the groove 9, and from a gap between the vane 4 and the cover 5 to lubricate these gaps and to seal the pump chamber 2A, and after that, the lubricating oil is discharged from the discharge passage 7 along with the gas.
  • the diameter direction gas hole 13a and the axial direction gas groove 13b simultaneously correspond to each other, and thus the atmosphere flows into the pump chamber 2A from this diameter direction gas hole 13a to eliminate the negative pressure therein, thereby enabling to prevent the large amount of lubricating oil from flowing into the pump chamber 2A.
  • a passage area of the gas passage 13 is defined as S 1
  • a passage area of the oil supply passage 11 is S 2
  • a passage area of the oil supply pipe 12 is S 3
  • a diameter of the diameter direction oil supply hole 11b is d 2
  • a width of the axial direction oil supply groove in a rotational direction of the rotor 3 is L
  • the passage area S 2 of the oil supply passage is set to be in a range of S 1 ⁇ S 2 ⁇ 3 ⁇ S 1
  • the passage area S 3 of the oil supply pipe is S 2 ⁇ S 3 ⁇ 3 ⁇ S 2
  • the width L of the axial direction oil supply groove is d 2 ⁇ L ⁇ 4 ⁇ d 2
  • the passage area S 1 of the gas passage 13 is set to be as small a passage area S 1 as possible in order to reduce the leakage of the lubricating oil to the outer space through the gas passage 13 when the hydraulic pressure of the lubricating oil supplied from the hydraulic pump to the oil supply passage 11 is high.
  • the passage area of the diameter direction gas hole 13a constituting the gas passage 13 is set as the passage area S 1
  • passage areas of the other axial direction gas grooves 13b constituting the gas passage 13 are respectively set to be larger than the passage area S 1 of the diameter direction gas hole 13a.
  • this diameter direction gas hole 13a is preferably as small as possible, it is preferable to employ, for example, a hole with a diameter of 1.5 millimeters in a balance with processing technology or cost, and in this case, the passage area S 1 of the diameter direction gas hole 13a is 1.77 mm 2 .
  • the passage area of the diameter direction oil supply hole 11b constituting the oil supply passage 11 is set as the passage area S 2 , and passage areas of the other axial direction oil supply holes 11a and axial direction oil supply grooves 11c constituting the oil supply passage 11 are all set to be larger than the passage area S 2 of the diameter direction oil supply hole 11b.
  • a passage area S 2 of the diameter direction oil supply hole 11b is 3.14 to 4.91 mm 2 .
  • the passage area S 2 of the oil supply passage 11 is made to be a relatively small passage area within 3 times larger than the small passage area S 1 of the gas passage 13, thereby enabling to make it difficult to suck the air. Meanwhile, the passage area S 2 of the oil supply passage 11 is set to be larger than the passage area S 1 of the gas passage 13, and thereby a required lubricating oil is made to be reliably supplied in the pump chamber 2A.
  • the passage area S 3 of the oil supply pipe 12 is set to be larger than the passage area S 2 of the above-mentioned oil supply passage 11.
  • the passage area S 3 of the oil supply pipe 12 is 9.62 mm 2 .
  • the passage area S 3 of the oil supply pipe 12 is set to be larger than the passage area S 2 of the oil supply passage 11, it can be expected to obtain a squeezing effect due to the oil supply passage 11, and thereby a hydraulic pressure in the oil supply passage 11 can be kept as high as possible even with a small amount of lubricating oil at the time of idling.
  • the width L of the axial direction oil supply groove 11c in the oil supply passage 11 is set in the range of d 2 ⁇ L ⁇ 4 ⁇ d 2 .
  • the width L of the axial direction oil supply groove 11c is larger than 2 millimeters, and falls in a range of less than 10 millimeters.
  • the width L of the axial direction oil supply groove is set to be too large, an overlap time of the diameter direction oil supply hole 11b and the axial direction oil supply groove 11c becomes longer, and particularly when the hydraulic pressure of the oil supply passage at the time of idling is low, the air is easily sucked due to vacuum of the pump chamber, and thus the width L of the axial direction oil supply groove is set to be in the above-described range to thereby suppress suck of the air.
  • Figures 4 and 5 are graphs showing test results, respectively.
  • Figure 4 is a test result graph obtained by testing a relation between the number of revolutions and driving torque, and it shows as a rate of torque reduction (%) how much driving torque of the exemplary vane pump of the present invention fluctuated with respect to amplitude of driving torque in a conventional example.
  • Figure 5 is a test result graph obtained by testing a relation between an oil supply amount to the pump chamber 2A and driving torque, and similarly to the case of Figure 4 , it shows as the rate of torque reduction (%) how much driving torque of the exemplary vane pump of the present invention fluctuated with respect to a test result of the conventional example.
  • a supply pressure of a lubricating oil is adjusted so that an oil supply amount may be 0.3 to 0.4L/m at each number of revolutions, and in the test of Figure 5 , the supply pressure of the lubricating oil is adjusted so that a supply amount shown in Figure 5 can be obtained while keeping the number of revolutions of the pump substantially constant (approximately 300 rpm).
  • a diameter of the diameter direction gas hole 13a is set to be 1.5 millimeters in each drawing (including the conventional example), and thus the passage area S 1 of the gas passage 13 is set to be 1.77 mm 2 .
  • a hole of 3.5 millimeters is employed for the passage area S 3 of the oil supply pipe 12, thus the passage area S 3 of the oil supply pipe 12 is set to be 9.62 mm 2 , and further, the width L of the axial direction oil supply groove 11c in the oil supply passage 11 is 7.5 millimeters.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (4)

  1. Pompe à palettes (1) comprenant :
    un boîtier (2) comprenant une chambre de pompe sensiblement circulaire (2A) ;
    un rotor (3) qui tourne autour d'une position excentrique par rapport à un centre de la chambre de pompe (2A) ;
    une palette (4) qui est tournée par le rotor (3) et qui sépare toujours la chambre de pompe (2A) en une pluralité d'espaces ;
    un passage de fourniture d'huile (11) qui communique par intermittence avec la chambre de pompe (2A) par la rotation du rotor (3) ;
    un tuyau de fourniture d'huile (12) qui est raccordé au passage de fourniture d'huile (11) pour fournir une huile de lubrification d'une pompe hydraulique à celui-ci ;
    et un passage de gaz (13) qui amène la chambre de pompe (2A) et un espace extérieur à communiquer l'un avec l'autre lorsque le passage de fourniture d'huile (11) communique avec la chambre de pompe (2A) par la rotation du rotor (3), dans laquelle
    le passage de fourniture d'huile (11) comprend :
    un trou de fourniture d'huile en direction du diamètre (11b) prévu sur une partie d'arbre (3B) du rotor (3) dans une direction du diamètre de celui-ci ; et
    une rainure de fourniture d'huile en direction axiale (11c) qui est prévue dans le boîtier (2) pour communiquer avec la chambre de pompe (2A), et avec laquelle une ouverture du trou de fourniture d'huile en direction du diamètre (11b) est amenée à communiquer par recouvrement par intermittence par la rotation du rotor (3), et
    le passage de gaz (13) comprend :
    un trou de gaz en direction du diamètre (13a) qui est prévu sur la partie d'arbre (3B) du rotor (3) dans la direction du diamètre de celui-ci pour communiquer avec le passage de fourniture d'huile (11) ; et
    une rainure de gaz en direction axiale (13b) qui est prévue dans le boîtier (2) pour communiquer avec l'espace extérieur, et avec laquelle une ouverture du trou de gaz en direction du diamètre (13a) est amenée à communiquer par recouvrement par intermittence par la rotation du rotor (3), et le trou de gaz en direction du diamètre (13a) est amené à communiquer avec la rainure de gaz en direction axiale (13b) lorsque le trou de fourniture d'huile en direction du diamètre (11b) est amené à communiquer avec la rainure de fourniture d'huile en direction axiale (11c), la pompe à palettes (1), dans laquelle
    lorsqu'une zone du passage de gaz (13) est définie en tant que S1, une zone du passage de fourniture d'huile (11) est S2, une zone de passage du tuyau de fourniture d'huile (12) est S3, un diamètre du trou de fourniture d'huile en direction du diamètre (11b) est d2, et une largeur de la rainure de fourniture d'huile en direction axiale (11c) dans une direction de rotation du rotor (3) est L, caractérisée en ce que la zone de passage S2 du passage de fourniture d'huile (11) est définie pour être plus grande que la zone de passage S1 du passage de gaz (13), et pas plus grande que trois fois la zone de passage S1 de sorte qu'une huile de lubrification requise soit amenée à être fournie de manière fiable dans la chambre de pompe (2A) via le passage de fourniture d'huile (11), et
    la zone de passage S3 du tuyau de fourniture d'huile (12) est définie pour être plus grande que la zone de passage S2 du passage de fourniture d'huile (11), et dans une plage entre deux et trois fois la zone de passage de S2, incluse de sorte qu'une pression hydraulique du passage de fourniture d'huile (11) puisse être maintenue élevée en raison d'un effet de compression même avec une petite quantité d'huile de lubrification, et
    en outre la largeur L de la rainure de fourniture d'huile en direction axiale (11c) est définie pour être plus grande que le diamètre du trou de fourniture d'huile en direction du diamètre d2, et plus petite que quatre fois le diamètre d2 pour supprimer l'aspiration de l'air dans la chambre de pompe (2A) lorsqu'une pression hydraulique du passage de fourniture d'huile (11) est basse.
  2. Pompe à palettes (1) selon la revendication 1,
    dans laquelle le passage de fourniture d'huile (11) est prévu dans le rotor (3) dans une direction axiale de celui-ci,
    et comprend un trou de fourniture d'huile en direction axiale (11a) communiquant avec le tuyau de fourniture d'huile (12), et le trou de fourniture d'huile en direction du diamètre (11b) communique avec ce trou de fourniture d'huile en direction axiale (11a).
  3. Pompe à palettes (1) selon la revendication 2,
    dans laquelle le trou de gaz en direction du diamètre (13a) communique avec le trou de fourniture d'huile en direction axiale (11a).
  4. Pompe à palettes (1) selon la revendication 1,
    dans laquelle la zone de passage S1 est de 1,77 mm2, la zone de passage S2 est de 3,14 mm2 à 4,91 mm2, la zone de passage S3 est de 9,62 mm2, le diamètre d2 est de 2 mm à 2,5 mm et la largeur L est de 2 mm à moins de 10 mm.
EP10846307.6A 2010-04-27 2010-11-17 Pompe à palettes Not-in-force EP2602487B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010102249A JP5447149B2 (ja) 2010-04-27 2010-04-27 ベーンポンプ
PCT/JP2010/070444 WO2011135747A1 (fr) 2010-04-27 2010-11-17 Pompe à palettes

Publications (3)

Publication Number Publication Date
EP2602487A1 EP2602487A1 (fr) 2013-06-12
EP2602487A4 EP2602487A4 (fr) 2016-05-18
EP2602487B1 true EP2602487B1 (fr) 2018-07-04

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EP10846307.6A Not-in-force EP2602487B1 (fr) 2010-04-27 2010-11-17 Pompe à palettes

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JP (1) JP5447149B2 (fr)
KR (1) KR101271036B1 (fr)
CN (1) CN102365462B (fr)
RU (1) RU2490516C2 (fr)
WO (1) WO2011135747A1 (fr)

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DE112013005092B4 (de) * 2012-10-22 2021-03-04 Hanon Systems Efp Deutschland Gmbh Kupplungsbeölung
ITTO20121157A1 (it) * 2012-12-27 2014-06-28 Vhit Spa Sistema di lubrificazione per una pompa per vuoto rotativa.
JP2014190312A (ja) * 2013-03-28 2014-10-06 Taiho Kogyo Co Ltd ベーンポンプのベーン
JP5799058B2 (ja) * 2013-07-30 2015-10-21 三桜工業株式会社 負圧ポンプ及びシリンダヘッドカバー
CN105492775B (zh) * 2013-10-07 2017-07-28 三樱工业株式会社 负压泵及缸盖罩
JP6210859B2 (ja) * 2013-11-22 2017-10-11 三桜工業株式会社 負圧ポンプ及びシリンダヘッドカバー
LV15039B (lv) * 2014-01-07 2015-09-20 Staņislavs MIROPOLECS Trohoidālais sūknis
US20180156218A1 (en) * 2015-06-02 2018-06-07 Pierburg Pump Technology Gmbh Automotive vacuum pump

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Publication number Priority date Publication date Assignee Title
SU383882A1 (ru) * 1971-01-08 1973-05-23 Авторы изобретени витель Роторный вакуумный насос-компрессор
RU2266430C2 (ru) * 2003-11-26 2005-12-20 Открытое акционерное общество Научно-производственное объединение "Искра" Агрегат компрессорный ротационно-пластинчатый
JP4733356B2 (ja) * 2004-03-10 2011-07-27 トヨタ自動車株式会社 気体用ベーンポンプおよびその運転方法
JP2006118424A (ja) * 2004-10-21 2006-05-11 Toyota Motor Corp バキュームポンプ
JP3874300B2 (ja) * 2005-02-16 2007-01-31 大豊工業株式会社 ベーンポンプ
JP3849799B2 (ja) * 2005-02-16 2006-11-22 大豊工業株式会社 ベーンポンプ
JP4022773B2 (ja) * 2005-02-16 2007-12-19 大豊工業株式会社 ベーンポンプ
JP2009185699A (ja) * 2008-02-06 2009-08-20 Toyota Motor Corp バキュームポンプ

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Also Published As

Publication number Publication date
CN102365462A (zh) 2012-02-29
US8449277B2 (en) 2013-05-28
WO2011135747A1 (fr) 2011-11-03
US20120156076A1 (en) 2012-06-21
CN102365462B (zh) 2014-10-15
EP2602487A1 (fr) 2013-06-12
JP2011231676A (ja) 2011-11-17
RU2011143786A (ru) 2013-05-10
KR20110125639A (ko) 2011-11-21
KR101271036B1 (ko) 2013-06-04
EP2602487A4 (fr) 2016-05-18
JP5447149B2 (ja) 2014-03-19
RU2490516C2 (ru) 2013-08-20

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